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EP1705395B1 - Joint homocinétique fixe - Google Patents

Joint homocinétique fixe Download PDF

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Publication number
EP1705395B1
EP1705395B1 EP06251417.9A EP06251417A EP1705395B1 EP 1705395 B1 EP1705395 B1 EP 1705395B1 EP 06251417 A EP06251417 A EP 06251417A EP 1705395 B1 EP1705395 B1 EP 1705395B1
Authority
EP
European Patent Office
Prior art keywords
cage
spherical
open end
joint
track grooves
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP06251417.9A
Other languages
German (de)
English (en)
Other versions
EP1705395A2 (fr
EP1705395A3 (fr
Inventor
Manabu Hoshino
Tohru Nakagawa
Hiroshi Tone
Wasaburo Suganuma
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2005082324A external-priority patent/JP2006266329A/ja
Priority claimed from JP2005084265A external-priority patent/JP2006266368A/ja
Priority claimed from JP2005089055A external-priority patent/JP4879501B2/ja
Priority claimed from JP2005198996A external-priority patent/JP2007016899A/ja
Priority claimed from JP2005204421A external-priority patent/JP2007024106A/ja
Priority claimed from JP2005214686A external-priority patent/JP2007032647A/ja
Priority claimed from JP2005214694A external-priority patent/JP2007032648A/ja
Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of EP1705395A2 publication Critical patent/EP1705395A2/fr
Publication of EP1705395A3 publication Critical patent/EP1705395A3/fr
Publication of EP1705395B1 publication Critical patent/EP1705395B1/fr
Application granted granted Critical
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Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D3/2237—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts where the grooves are composed of radii and adjoining straight lines, i.e. undercut free [UF] type joints
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22303—Details of ball cages
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S464/00—Rotary shafts, gudgeons, housings, and flexible couplings for rotary shafts
    • Y10S464/904—Homokinetic coupling
    • Y10S464/906—Torque transmitted via radially spaced balls

Definitions

  • the present invention relates to fixed-type constant velocity universal joints.
  • Constant velocity universal joints are used in the power transmission of automobiles and various industrial machines and transmit torque from a driving shaft to a driven shaft at a constant angular velocity.
  • Two types of constant velocity universal joints are known: fixed-type, which permits only angular displacement, and slidable-type, which permits both angular and axial displacement.
  • a typical fixed-type constant velocity universal joint includes the following components: an outer joint member that is connected to a driving or driven shaft in a torque-transmitting manner; an inner joint member that is connected to the driven or driving shaft in a torque-transmitting manner; a plurality of balls placed between the outer and inner joint members to transmit torque; and a cage that holds the balls within the bisecting-plane of the angle between the driving and driven shafts.
  • FR-2798709 discloses the preamble of claim 1.
  • a fixed-type constant velocity universal joint of the present invention is provided in accordance with claim 1.
  • the present invention achieves the above-described object by defining, of all the internal dimensions of fixed-type constant velocity universal joints, the optimum geometry of the cage that takes into account the interference between the rise formed along the edge of the track grooves and the spherical cage surface and is adapted to prevent excessive stress from being applied to the pockets at their corners away from the open end of the joint.
  • a fixed-type constant velocity universal joint of the present invention comprises:
  • This construction in which the radius of curvature at the corners of the pockets away from the open end of the joint is larger than the radius of curvature at the corners adjacent to the open end and is smaller than the ball radius, can reduce the stress applied to the corners of the pockets away from the open end of the joint when the rise formed along the edge of the track grooves interferes with the spherical cage surfaces.
  • the stress balance can be optimized between the corners of the pockets away from the open end of the joint and the corners adjacent to the open end of the joint. This ensures cage strength.
  • the pockets have a equal or smaller radius of curvature at the corners away from the open end of the joint to or than that at the corners adjacent to the open end of the joint, then it is difficult to reduce the excessive stress applied to the corners away from the open end. If the radius of curvature at the corners of the pockets away from the open end of the joint is equal to or larger than the ball radius, then the balls may interfere with the corners of the pockets away from the open end of the joint when the balls come into contact with the pillars between the pockets.
  • the ratio f/PCR have a value greater than zero and smaller than or equal to 0.12, given that the cage offset amount between the center of the spherical outer surface and the center of the spherical inner surface of the cage is f, and the length of the line segment connecting the center of the curvature of the track grooves of the outer joint member or the center of the curvature of the track grooves of the inner joint member with the ball center is PCR.
  • the strength of the cage can be improved by increasing the thickness of the cage at its open end from which to insert the inner joint member.
  • the cage pockets can confine the balls and keep them from coming out of the outer joint member from its open end when the joint is operated at larger operating angles.
  • the cage offset is too large, then the circumferential displacement of the balls within the cage pockets become large, so that the size of the cage pockets must be increased along the circumference of the cage in order to ensure proper movement of the balls.
  • the width of the pillars of the cage is decreased, resulting in a decreased strength of the cage.
  • the thickness of the cage is decreased in the area away from its open end. This also results in a decreased strength of the cage.
  • the optimum range for the cage offset amount can vary depending on the size of the joint and must therefore be determined by considering the base dimensions of the joint that are reflecting the size of the joint.
  • the ratio f/PCR of the cage offset amount f to the length PCR of the line segment that connects the center of the curvature of the track grooves of the outer joint member or the center of the curvature of the track grooves of the inner joint member with the ball center is used.
  • the cage offset amount in the above-described construction is preferably set such that the ratio f/PCR has a value greater than zero and smaller than or equal to 0.12, given that the cage offset amount is f and the length of the line segment connecting the center of the curvature of the track grooves of the outer joint member or the center of the curvature of the track grooves of the inner joint member with the ball center is PCR. Since the cage offset amount f is a function of the difference in the thickness of the cage wall as viewed in the longitudinal section, it is preferably determined by considering this amount.
  • the ratio f/PCR is greater than 0.12, then the above-described problems concerning the strength may arise. Conversely, if the ratio is smaller than or equal to zero, then the advantages of the cage offset amount may be lost.
  • the cage offset which is intended to prevent the contact point of the balls at the open end of the outer joint member from coming out of the cage pocket when the joint is operated at larger operating angles, cannot achieve its desired purpose when it has a value equal to or less than zero.
  • the optimum range for the cage offset amount f is such that the ratio f/PCR is equal to or smaller than 0.12 in order to ensure the strength and durability of the cage.
  • the track grooves of the outer and inner joint members are preferably finished by cold forging.
  • the finishing of the tapered track grooves with cold forging facilitates removal of the mold.
  • the employment of cold forging not only improves workability but also reduces the manufacturing cost.
  • a fixed-type constant velocity universal joint comprises an outer ring 10, an inner ring 20, a ball 30 and a cage 40.
  • the fixed-type constant velocity universal joint connects two shafts to be connected.
  • a driven shaft (not shown) is connected to the outer ring 10, to which a driving shaft (not shown) is connected so that the torque is transmitted at constant velocity from the driving shaft to the driven shaft when the two shafts are at an angle to each other.
  • Fig. 1 shows the state in which the operating angle ⁇ that the rotation axis X of the outer ring 10 makes with the rotation axis Y of the inner ring 20 is 0°
  • Fig. 1 shows the state in which the operating angle ⁇ is at its maximum.
  • the outer ring 10 to serve as the outer joint member consists of a mouth portion 16 and a stem portion (not shown) that is coupled to the driving shaft in a torque-transmitting manner.
  • the mouth portion 16 is essentially a cup with an open end and has a spherical inner surface 12 that has a plurality of axially extending, circumferentially equally spaced track grooves 14 formed thereon. Each track groove 14 extends to the open end 18 of the mouth portion 16.
  • the inner ring 20 to serve as the inner joint member has a spherical outer surface 22 that includes a plurality of axially extending, circumferentially equally spaced track groves 24 formed thereon. Each track groove 24 is axially cut across the inner ring 20.
  • the inner ring 20 has a splined bore 26 to connect the inner ring to the driving shaft in a torque-transmitting manner.
  • the track grooves 14 of the outer ring 10 are formed to correspond to the track grooves 24 of the inner ring 20.
  • Each pair of corresponding grooves 14, 24 forms a ball track in which a ball 30 is rollably received to transmit torque.
  • the balls 30 are arranged between the track grooves 14 of the outer ring 10 and the track grooves 24 of the inner ring 20 to transmit torque from the inner ring to the outer ring.
  • the balls 30 are received in corresponding pockets 46 arranged along the circumference of the cage 40.
  • the number of the balls 30 and thus, the number of the track grooves 14, 24 may be any suitable number, for example, 6 or 8.
  • the cage 40 is slidably arranged between the outer ring 10 and the inner ring 20 and has a spherical outer surface 42 in contact with the spherical inner surface 12 of the outer ring 10 and a spherical inner surface 44 in contact with the spherical outer surface 22 of the inner ring 20.
  • the curvature of the spherical inner surface 12 of the outer ring 10 and the curvature of the spherical outer surface 42 of the cage 40 have the same center (denoted by 'O 4 ' in Fig. 2 ).
  • the curvature of the spherical outer surface 22 of the inner ring 20 and the curvature of the spherical inner surface 44 of the cage 40 have the same center (denoted by 'O 3 ' in Fig. 2 ).
  • the gap between the spherical inner surface 12 of the inner ring 10 and the spherical outer surface 42 of the cage 40 is shown out of scale for clarity, as is the gap between the spherical outer surface 22 of the inner ring 20 and the spherical inner surface 44 of the cage 40.
  • Each of the track grooves 14 of the outer ring 10 includes an arc portion 14a and a linear portion 14b with the arc portion 14a formed on the deeper side, or on the side away from the open end of the mouth portion 16, and the linear portion 14b on the side of the open end.
  • Each track groove 14 has its bottom linearly tapered by an angle ⁇ in the area adjacent to the open end 18 so that the depth of the groove increases toward the open end 18.
  • Each of the track grooves 24 of the inner ring 20 includes an arc portion 24a and a linear portion 24b with the arc portion 24a formed on the open end side of the outer ring 10 and the linear portion 24b on the side away from the open end.
  • Each track groove 24 has its bottom linearly tapered by an angle ⁇ in the area away from the open end so that the depth of the groove increases toward the end opposite to the open end.
  • This joint has a construction as shown in Fig. 2 to ensure large operating angle ⁇ of the joint.
  • the center of the curvature O 1 of the track grooves 14 of the outer ring 10 is offset from the center O 3 of the spherical inner surface 12 by a distance F
  • the center of the curvature O 2 of the track grooves 24 of the inner ring 20 is offset from the center O 4 of the spherical outer surface 22 by the same distance F (i.e., Track offset).
  • the center of the curvature O 1 and the center of the curvature O 2 are offset from the corresponding centers of the spherical surfaces in the axially opposite direction.
  • the center of the curvature O 3 of the spherical outer surface 42 of the cage 40 and the center of the curvature O 4 of the spherical inner surface 44 of the cage 40 are oppositely offset from the center of the joint O by an equal distance f along the axis direction (i.e., cage offset).
  • Each of the ball tracks formed by the corresponding pairs of track grooves 12, 24 of the outer ring 10 and the inner ring 20 has a "wedge-like" shape with the narrow end relatively inside the mouth portion 16 of the outer ring 10 gradually widening toward the open end of the outer ring 10.
  • a force is applied to the ball 30 that urges the ball from the narrow end to the wide end of the wedge-like ball track (indicated in Fig. 2 by a blank arrow).
  • the load exerted by this urging force upon the wall of the pockets 46 of the cage 40 is referred to as "pocket load,” hereinafter.
  • the present joint is designed to have a larger cage offset amount f as compared to conventional universal joints so that the cage 40 serves to confine the balls 30 and keep them from coming out of the mouth portion 16 of the outer ring 10 from the open end 18 when the joint is operated at the maximum operating angle.
  • the cage offset amount f is determined so that the ratio f/PCR has a value greater than 0 and smaller than or equal to 0.12, given that the radius of the trajectory of the center of the ball 30 (or the length of the line segment connecting the center of the curvature O 1 of the track grooves 14 of the outer ring 10 or the center of the curvature O 2 of the track grooves 24 of the inner ring 20 with the center O 5 of the ball 30) is PCR.
  • track load refers to the load exerted by the contacting ball 30 upon the wall of the track grooves 14, 24.
  • a spherical force (i.e ., force acting between spherical surfaces) acts between the cage 40 and the outer ring 10 or the inner ring 10 during torque transmission.
  • the above-described construction lowers the maximum value of the spherical force and thus decreases the heat generated within the joint. In addition, this construction facilitates removal of the mold, ensuring high workability during cold forging and reducing manufacturing cost.
  • the force with which the ball 30 urges the cage 40 toward the open end increases (indicated in Fig. 2 by blank arrow).
  • the spherical outer surface 42 of the cage 40 is vigorously rubbed against the spherical inner surface 12 of the outer ring 10 in the area adjacent to the open end of the outer ring (indicated in Fig. 3 by "A").
  • the cage 40 is in contact with the outer ring 10 only in a small area, a significant amount of heat is generated, causing reduced durability and the loss of torque transmission.
  • Fig. 5 illustrates the state in which the operating angle ⁇ that the rotation axis X of the outer ring 10 makes with the rotation axis Y of the inner ring 20 is 0°
  • Fig. 6 illustrates the state in which the operating angle ⁇ is largest.
  • the end of the spherical outer surface 142 adjacent to the open end of the outer ring is axially extended, in contrast to the cage 40 of the joint shown in Fig. 1 , and a tapered surface 148 is formed at the end of the spherical inner surface 144 adjacent to the open end of the outer ring.
  • the surface 148 is tapered in such a manner that the tapered surface has an increasing diameter toward the end of the spherical outer surface 142 adjacent to the open end of the outer ring ( Figs. 1 and 5 ). As shown in Fig.
  • the end of the spherical outer surface 142 of the cage 140 adjacent to the open end of the outer ring 20 is extended by an amount that prevents the interference of the shaft 50, which is attached to the inner ring 20 via spline engagement, with the end of the cage 140 adjacent to the open end of the outer ring while the outer ring 10 makes the maximum operating angle with the inner ring 20.
  • the taper angle ⁇ /2 of the tapered surface 148 is half the maximum operating angle ⁇ or larger, then the spherical outer surface 142 of the cage 140 is kept in contact with the spherical inner surface 12 of the outer ring 10 in a sufficiently large area when the joint is operated at larger operating angles. If the taper angle ⁇ /2 is smaller than half the maximum operating angle 8, then the shaft 50 will interfere with the end of the cage 140 adjacent to the open end of the outer ring.
  • the spherical outer surface 142 of the cage 140 is kept in contact with the spherical inner surface 12 of the outer ring 10 in a sufficiently large area ensures that the balls 30 urge the cage 140 toward the open end when the joint is operated at the maximum operating angle ⁇ .
  • the decrease in the durability or the loss of torque transmission caused by the generated heat can be minimized when the end of the spherical outer surface 142 of the cage 140 adjacent to the open end of the outer ring vigorously rubs against the spherical inner surface 12 of the outer ring 10.
  • This construction also ensures maximum rigidity of the cage 140, so that the strength of the cage 140 is also improved.
  • the edge 143 of the pocket 146 that connects the spherical inner cage surface 144 to the end surface 141 of the pocket 146 may be filleted to form, for example, spherical R curve, as shown in Fig. 7 .
  • the spherical R curve is a continuous spherical surface that smoothly connects between the spherical inner surface 144 of the cage 140 and the end surface 141 of the pocket 146.
  • the edge 143 on the spherical inner surface-side of the cage is formed along the entire circumference of the pocket 146.
  • Fig. 8 shows one example in which the edge 143 on the cage spherical inner surface-side of the pocket 146 is formed as spherical R curve as is the edge 145 on the cage spherical outer surface-side.
  • the spherical R curve of the edge 145 on the cage spherical outer surface-side is also a continuous spherical surface that smoothly connects between the spherical outer surface 142 of the cage 140 and the end surface 141 of the pocket 146.
  • the edge 145 is also formed along the entire circumference of the pocket 146.
  • This construction in which the edges 143, 145 of the pockets 146 are formed as spherical R curve on the spherical inner surface-side or on the'spherical outer surface-side of the cage, prevents cracking and chipping of the edges 143, 145 of the pockets 146 when dynamic twisting torque higher than the permissive level is applied to the joint and the rise formed along the edge of the track grooves of the outer ring 10 and the inner ring 20 interferes with the spherical inner surface 144 and the spherical outer surface 142 of the cage 140. As a result, the strength of the cage 140 is ensured.
  • the cage 140 includes a plurality of substantially rectangular pockets 146 arranged along its circumference with each pocket 146 having four corners: two "thin area-side” corners 147 and two "thick area-side” corners 149.
  • Fig. 9 shows one embodiment in which each pocket 146 of the cage 140 has a larger radius of curvature at the thin area-side corners 147 thereof than at the thick area-side corners 149 and the radius of curvature is smaller than the radius of the ball 30.
  • a single pocket 146 is shown in Fig. 10 in its planer view for easy comparison of the radius of curvature between the thin area-side corners 147 and the thick area-side corners 149 of the pocket 146.
  • Fig. 11 shows another embodiment in which the thin area-side corners 147 of the pocket 146 have a minimum radius of curvature (R min ), which is the same radius of curvature as the thick area-side corners 149.
  • Fig. 12 shows another embodiment in which the thin area-side corners 147 of the pocket 146 have a maximum radius of curvature (R max ), which is the same radius as the ball 30.
  • This construction in which the radius of curvature at the thin area-side corners 147 of the pockets 146 is larger than the radius of curvature at the thick area-side corners 149 and is smaller than the radius of the ball 30, can reduce the stress applied to the thin area-side corners 147 of the pockets 146 when the rise formed along the edge of the track grooves interferes with the spherical inner surface 144 and the spherical outer surface 142 of the cage 140 and confines the movement of the cage 140. As a result, the stress balance can be optimized between the thin area-side corners 147 and the thick area-side corners 149. This ensures the strength of the cage 140. '
  • the track offset is relatively small, whereas the cage offset is relatively large to ensure operation of the joint at larger operating angles. Due to the small track offset, the track grooves 14 of the outer ring 10 can be constructed to have sufficient depth in the deeper side area. This helps prevent the ball 30 in the innermost position of the track groove 14 from running off the groove.
  • the small track offset results in a small embrace angle (spherical angle) ⁇ , the angle by which the outer ring 10 embraces the cage 40 (see Fig. 2 ).
  • the term "embrace angle (spherical angle) ⁇ " refers to the angle that the end of the spherical inner surface 12 of the outer ring 10 adjacent to the open end makes with the joint midplane P.
  • the spigot diameter ⁇ D 1 of the outer ring 10 ( Fig. 1 ) is made equal to or larger than the outermost diameter ⁇ D 2 of the cage 40 ( Fig. 4 ). This, however, makes the embrace angle (spherical angle) ⁇ of the outer ring 10 even smaller. As a result, the strength and durability of the joint may be decreased and torque transmission may be lost.
  • the geometry of the cage 140 is optimized as in the joint shown in Fig. 5 .
  • the cage 140 of Fig. 5 as viewed from the opposite side of the open end of the outer ring 10 is shown in Fig. 13 and a sectional view of Fig. 13 is shown in Fig. 14 .
  • the cage 140 of the joint shown in Fig. 5 has part of its spherical outer surface 142 cut on the open end side of each pocket 146 to form a planar cut face 150.
  • the outer diameter ⁇ D 4 of the cage 140 across the two opposing planar cut faces 150 is smaller than the spigot diameter ⁇ D 3 of the outer ring 10 (see Figs. 5 and 6 ).
  • part of the spherical outer surface 142 is cut on the open end side of the pockets 146 so that the contact point of the cage with the ball 30 exists when the joint is operated at the rotation axis X of the outer ring 10 making the maximum operating angle ⁇ with the rotation axis Y of the inner ring 20.
  • the cut face 150 is formed for each of the circumferentially equally spaced pockets 146 as shown in Fig. 13 and Fig. 14 , the cut face may not be formed for each pocket 146: It may be formed for at least an opposing pair of the pockets 146.
  • the reason that the cut is made for at least two opposing pockets 146 is as follows: During assembly of the cage 140 with the outer ring 10 as depicted in Fig. 15 , the cage 140 is first inserted into the outer ring 10 with its axis kept perpendicular to the axis of the outer ring 10. After insertion into the outer ring 10, the cage 140 is turned by 90° so that its axis is aligned with the axis of the outer ring 10. The insertion of the cage 140 into the outer ring 10 is possible if the partial cut is made for at least two opposing pockets 146 and the outer diameter ⁇ D 4 of the cage 140 across the two planar cut faces 150 is smaller than the spigot diameter ⁇ D 3 of the outer ring 10.
  • part of the spherical outer surface 142 of the cage 140 on the open end side of the pockets 146 is cut to form a planar cut face 150, and the outer diameter ⁇ D 4 of the cage 140 across the two planar cut faces 150 is smaller than the spigot diameter ⁇ D 3 of the outer ring 10.
  • This construction makes it possible to ensure the strength of the cage 140 and at the same time construct the cage 140 with a decreased diameter ⁇ D 4 [which is smaller than the outermost diameter ⁇ D 2 of the cage 40 of the joint shown in Fig. 1 ( Fig. 16b )], as shown in Fig.
  • the outer ring 10 with a decreased spigot diameter ⁇ D 3 of the outer ring 10 (which is smaller than the spigot diameter ⁇ D 1 of the outer ring 10 of the joint shown in Fig. 1 ). Accordingly, the embrace angle (spherical angle) ⁇ of the outer ring 10 (see Fig. 6 ) is not decreased, so that the assembly of the cage 140 with the outer ring 10 can be facilitated without decreasing the strength or durability of the joint or losing torque transmission.
  • the term "variation" indicates the difference between the maximum and the minimum of the spherical force.
  • Fig. 17 shows the relationship between the taper angle ⁇ (deg) and the joint strength.
  • the upper limit of the optimum taper angle ⁇ is determined to be 12°.
  • the arc portion 14a of the track groove 14 of the outer ring 10 arranged farther inside the mouth portion 16 can be formed with a uniform depth. Accordingly, the ball 30 in its innermost position in the track groove 14 of the outer ring 10 is kept from running off the groove when the joint is operated at larger operating angles.
  • the track offset amount F was fixed to zero (no track offset) in view of the performance of the ultrahigh operating angle fixed-type constant velocity universal joints by which permissive load torque does not decrease when the joint is operated at high operating angles.
  • the cage offset is preferably kept as small as possible in terms of internal force, minimal cage offset is still required in order to ensure proper functioning of the joint.
  • the cage offset was varied within the following range: 0 ⁇ f/PCR ⁇ 0.150.
  • the taper angle ⁇ was varied between 0 deg and 12 deg.
  • Fig. 18 is constructed based on the data obtained in the internal force analysis with the horizontal axis representing the taper angle ⁇ (deg) and vertical axis representing f/PCR.
  • the internal specifications of the joint that can minimize the load exerted in the 0 deg phase and are advantageous during operation at larger operating angles can be determined as follows:
  • the cage 40 is preferably placed in the outer ring 10 with its thick portion facing the open end 18.
  • Such an arrangement of the cage can ensure joint strength since the load applied in the 0 deg phase is decreased whereas the peak load is increased as compared to conventional constant velocity universal joints.
  • the joint of Example was operated at a larger operating angle (56°) than the joint of Comparative Example (50°).
  • the exerted stress was lower in the joint of Example than in the joint of Comparative Example, indicating that the cage of the present invention having the above specifications has comparable or higher strength than the cage of Comparative Example when the joint is operated at larger operating angles than the joint of Comparative Example.
  • the increase in the maximum pocket load in Example was considered to be caused by tapering of the track grooves and increased operating angle.
  • the following cage specifications are employed so that the joint can withstand the increased pocket load and premature breakage of the joint can be avoided.
  • the figures in the brackets are specifications for conventional fixed-type constant velocity universal joints (BJ) or fixed-type constant velocity universal joints (UJ).
  • the outer diameter Do, inner diameter Di, and width w are as shown in Fig. 2 .
  • the cage thickness t is the thickness measured at the center of the cage along the central axis.
  • the ratio (Di/d) of the cage inner diameter (Di) to the ball diameter (d) is determined from the cage outer diameter and the cage thickness. For reference, the ratio is as follows: 3.25 ⁇ Di / d ⁇ 3.45 3.10 ⁇ Di / d ⁇ 3.25 .
  • the pocket load acts in the direction that goes from the inside of the mouth portion of the outer ring to the open end of the outer ring
  • the cage is placed in the outer ring so that the thick end of the cage is adjacent to the open end and the thin end of the cage is inside the mouth portion of the outer ring. This is because of the need to form an appropriate spigot diameter for the assembly of inner ring.
  • the pocket load that acts in the direction that goes from the open end of the outer ring to the inside of the mouth portion of the outer ring is relatively minor and causes no particular problems.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Pivots And Pivotal Connections (AREA)

Claims (3)

  1. Joint homocinétique du type fixe, comprenant :
    un élément de joint externe (10), comportant une surface sphérique interne (12) avec une extrémité ouverte (18) et plusieurs rainures formant piste (14) formées sur la surface sphérique interne (12), les rainures formant piste (14) s'étendant chacune le long d'une direction axiale vers l'extrémité ouverte et étant espacées de manière régulière le long de la circonférence de la surface sphérique interne (12) ;
    un élément de joint interne (20), comportant une surface sphérique externe (22) et plusieurs rainures formant piste (24), correspondant aux rainures formant piste (14) de l'élément de joint externe (10), formées sur la surface sphérique interne (12), les rainures formant piste (24) s'étendant chacune le long de la direction axiale et étant espacées de manière régulière le long de la circonférence de la surface sphérique externe (22) ;
    plusieurs billes (30), reçues dans les rainures formant piste respectives (14, 24) des éléments de joint externe (10) et interne (20), de sorte à transmettre un couple ; et
    une cage (40) pour contenir les plusieurs billes (30), la cage (40) étant agencée entre la surface sphérique interne (12) de l'élément de joint externe (10) et la surface sphérique externe (22) de l'élément de joint interne (20), la cage (40) comportant une surface sphérique externe (42) et une surface sphérique interne (44) ; dans lequel :
    un centre de la surface sphérique externe (42) de la cage (40) et un centre de la surface sphérique interne (44) de la cage (40) sont décalées de manière opposée d'un centre du joint par une distance égale le long de la direction axiale ;
    une paroi de la cage (40), vue en section longitudinale, est relativement épaisse dans une région adjacente à l'extrémité ouverte (18) de l'élément de joint externe (10) et est relativement fine dans une région située à l'écart de l'extrémité ouverte (18) ;
    les rainures formant piste (14) de l'élément de joint externe (10) comportent chacune un fond effilé de manière linéaire dans une région adjacente à l'extrémité ouverte, de sorte qu'une profondeur des rainures est accrue en direction de l'extrémité ouverte (18) ;
    les rainures formant piste (24) de l'élément de joint interne (20) comportent chacune un fond effilé de manière linéaire dans une région située à l'écart de l'extrémité ouverte, de sorte qu'une profondeur des rainures est réduite en direction de l'extrémité de l'élément de joint interne (20) opposée à l'extrémité ouverte (18) ; et
    caractérisé en ce que
    plusieurs poches essentiellement rectangulaires (46), agencées le long de la circonférence de la cage (40) et recevant les billes (30), présentent un rayon de courbure au niveau de leurs coins écartés de l'extrémité ouverte (18) de l'élément de joint externe (10), le rayon de courbure étant plus grand qu'au niveau des coins adjacents à l'extrémité ouverte (18) et plus petit qu'un rayon de la bille (30).
  2. Joint homocinétique du type fixe selon la revendication 1, dans lequel un rapport f/PCR a une valeur supérieure à zéro et inférieure ou égale à 0,12, étant donné que la distance de décalage de la cage entre le centre de la surface sphérique externe (42) et le centre de la surface sphérique interne (44) de la cage (40) correspond à f, une longueur d'un segment de ligne connectant le centre de courbure des rainures formant piste (14) de l'élément de joint externe (10) ou le centre de courbure des rainures formant piste (24) de l'élément de joint interne (20) au centre de la bille correspondant à CPR.
  3. Joint homocinétique de type fixe selon les revendications 1 ou 2, dans lequel les rainures formant piste (14, 24) des éléments de joint externe et interne (10, 20) sont soumises à une finition par forgeage à froid.
EP06251417.9A 2005-03-22 2006-03-16 Joint homocinétique fixe Active EP1705395B1 (fr)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
JP2005082324A JP2006266329A (ja) 2005-03-22 2005-03-22 固定型等速自在継手
JP2005084265A JP2006266368A (ja) 2005-03-23 2005-03-23 固定式等速自在継手
JP2005089055A JP4879501B2 (ja) 2005-03-25 2005-03-25 高角固定式等速自在継手
JP2005198996A JP2007016899A (ja) 2005-07-07 2005-07-07 固定型等速自在継手
JP2005204421A JP2007024106A (ja) 2005-07-13 2005-07-13 固定型等速自在継手
JP2005214686A JP2007032647A (ja) 2005-07-25 2005-07-25 高角固定式等速自在継手
JP2005214694A JP2007032648A (ja) 2005-07-25 2005-07-25 高角固定式等速自在継手

Publications (3)

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EP1705395A2 EP1705395A2 (fr) 2006-09-27
EP1705395A3 EP1705395A3 (fr) 2009-08-19
EP1705395B1 true EP1705395B1 (fr) 2014-05-07

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EP (1) EP1705395B1 (fr)

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Also Published As

Publication number Publication date
US20060217207A1 (en) 2006-09-28
EP1705395A2 (fr) 2006-09-27
US8147342B2 (en) 2012-04-03
EP1705395A3 (fr) 2009-08-19

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